Ring rolling machine



June 1, 1965 o, u cl- 3 ,186102 RING ROLLING MACHINE Filed Dec. 18, 1962I 6 Sheets-Sheet 1 Fig! Jnrenlor: Odo ulcfafi June 1, 1965 o. ULRYCH3,186,202

RING ROLLING MACHINE Filed Dec. 18, 1962 e Sheets-Sheet 2 In ran for: @a21? June 1, 1965 o. ULRYCH 6 Sheets-Sheet 3 Fig. 3

Jnren for: 040 rips/7 June 1, 1965 o. umvcl-l RING ROLLING MACHINE 6Sheets-Sheet 4 Filed Dec. 18, 1962 Jnvenior: ofiio 2t a; b 6

June 1, 1965 o. ULRYCH RING ROLLING MACHINE 6 Sheets-Sheet 5 Filed Dec.18, 1962 ma me x% H& M 1.. w a

an mu m Nw mm Nu United States Patent ,34 21 Claims. (Cl. 7210) Thepresent invention relates to a ring rolling machine, and moreparticularly to a ring rolling machine including a first pair of rollersrolling the outer and inner peripheral surfaces of an annular blank anda second pair of rollers for rolling the annular end faces of the blank.

Ring rolling machines of this type serve the purpose of increasing thediameter of an annular blank. In accordance with the prior art, rollersacting on the axial end faces of the blank determine the coaxial heightof the finished ring, but are incapable of rolling the blank to reducethe axial height of the same.

It is one object of the present invention to provide a ring rollingmachine in which an annular blank is rolled to reduce the axial heightthereof.

Another object of the invention is to provide a rapidly and economicallyoperating ring rolling machine in which the rollers are not worn bymovement relative to the blank and corresponding frictional engagement.

Another object of the invention is to provide a ring rolling machinerequiring less power than conventional ring rolling machines.

With these objects in view one embodiment of the invention comprisesfirst roller means for engaging and rolling the inner and outerperipheral surfaces of an annular blank for increasing the diameter ofthe same; second roller means for engaging and rolling a portion of theaxial end faces of the annular blank; supporting means supporting thesecond roller means for movement in the direction in which the axial endfaces move outwardly as the diameter of the blank increases; sensingmeans including feeler means for engaging one peripheral surface of theblank; and control means controlled by the sensing means and causingmovement of the supporting means and of the second roller means at aspeed related to the displacement of the sensing means so that thesecond roller means remain in rolling engagement with the blank as thediameter of the blank increases.

The sensing means are preferably mechanical feeler means, but optical orpneumatic sensing means may also be used. Limit switches are controlledby the sensing means and effect control operations of electromagneticelements provided in hydraulic circuits.

Preferably the position of the sensing means on the supporting means canbe adjusted in accordance with a type of blank rolled in the machine.

The limit switch can be set to a desired final diameter of the blank,and the rolling operation is automatically terminated when the blank hasa desired diameter and exactly circular shape.

In the preferred embodiment of the invention, the second roller meansare frusto-conical roller mounted on a carriage, one of thefrusto-conical rollers being mounted on a slide provided on thecarriage.

One of the frusto-conical rollers is driven from a motor through avariable transmission so that its rotary speed, and peripheral speed canbe adjusted to the circumferential speed of the rotating blank.Preferably, the peripheral speed of the frusto-conical rollers isslightly higher than the circumferential speed of the blank at thebeginning of the operation.

The frusto-conical rollers are controlled from the sensing means so thatthe base circles roll on the outermost portions of the annular endfaces, irrespective of the increase of the diameter of the blank.

The novel features which are considered as characteristic for theinvention are set forth in particular in the appended claims. Theinvention itself, however, both as to its construction and its method ofoperation, together with additional objects and advantages thereof, willbe best understood from the following description of specificembodiments when read in connection with the accompanying drawings, inwhich:

FIG. 1 is a side elevation of a ring rolling machine according to thepresent invention;

F FIG. 2 is a plan view of the machine illustrated in FIG. 3 'is asectional view taken on line III-III in FIG. 2, but illustrating themachine in an operative position; 7

FIG. 4 is a diagrammatic view including a fragmentary plan view,partially in horizontal section, and a diagram of a hydraulic circuit,and illustrating apparatus required for actuating a first rollingdevice;

FIG. 5 is a diagrammatic view including a fragmentary side elevation,partially in section, and a diagram of a second hydraulic circuit, andillustrating apparatus required for actuating a second rolling device;

FIG. 6 is a diagrammatic view including a fragmentary horizontalsectional view, and a diagram of a third hydraulic circuit, andillustratiing apparatus required for operating movable supporting meansfor the second rolling device;

FIG. 7 is a fragmentary schematic side elevation illustrating theposition of the rolling devices at the beginning of an operation; and

FIG. 8 is a fragmentary schematic side elevation illustrating theposition of the rolling devices at the end of an operation.

Referring now to the drawings, a main shaft 2 supports a main roller 3and is rotatably mounted in the frame 1 of the machine. A pair ofcentering rolls 6, 7 are mounted on a pair of lever arms 8 and 9 whichare mounted on the frame 1 of the machine and can be moved toward andaway from the main roller 3 for centering an annular blank 38 in theposition of FIG. 4, lever means 8, 9 being omitted in FIG. 4 for thesake of clarity.

A carriage 12 is mounted on frame 1 for movement along guideways 10, 11and has a rectangular opening through which the main shaft 2 passes. Arectangular frame 16 is mounted on carriage 12, and can be operated by ahydraulic servomotor 15 to perform a pivotal movement between a raisedposition and a position in which a bearing 16a abuts the upper end of aroller 13 whose shaft is rotatably supported in a bearing 14 on carriage12. When frame 16 is raised, the annular blank 38 can be placed in theposition shown in FIG. 7, whereupon the frame 16 is lowered so thatbearing 16a is pressed against the upper end of roller 13 to support,the same during the following rolling operation in which the annularblank 38 will be rolled between rollers 3 and 13. During such rollingoperation, the diameter of the annular blank increases, and at the endof the rolling operation the annular blank has far greater inner andouter diameters, as shown in FIG. 8.

Carriage 12 is moved in the plane defined by the axes of rollers 3 and13 by means of the hydraulic servomotor which includes a cylinder 17secured to carriage 12, and a piston means 18 secured to frame 1. Pistonmeans 18 forms two chambers in cylinder 17, which can be supplied withpressure fluid through openings 19 and 20. Piston means 18 has alongitudinally extending cylinder bore in which an auxiliary piston 21is mounted,

one end of the auxiliary piston 21 abutting one end wall of cylinder 17.

A carriage 22 is mounted on the other end of frame 1, and is slidablealong guideways in the direction of the plane in which the axes ofrollers 3 and 4 are located. Such movement is effected by a hydraulicservomotor including a double-acting cylinder 24 secured to frame 1, anda piston 23, best seen in FIG. 3 which is movable in cylinder 24.

A frusto-conical roller 25 is mounted for rotation on carriage 22, andis driven by motor 26 through a shiftable transmission 27 schematicallyindicated in FIG. 3.

When the annular blank is rolled between rollers 3 and 13, its diameterincreases, and consequently the circumferential speed of the portion ofthe axial end face of blank 38 engaged by roller 25 will increase. Thespeed of motor 26, and the corresponding speed of roller 25, is selectedin such a manner that the peripheral speed of roller 25 is slightlygreater than the circumferential speed of the axial end face of theblank engaged thereby when a new blank is placed in the machine, and arolling operation is started. As the diameter of the blank increasesduring the rolling operation, its circumferential speed will increase,and will become the same as the peripheral speed of the roller 25, whichwas too high at the beginning of the rolling operation. The transmissionmeans 27 are shiftable to effect rotation of roller 25 at differentrotary speeds, so that the peripheral speed of roller 25 can beadjusted.

In a preferred embodiment of the invention, the peripheral speed at thegreatest diameter of roller 25 is 6% greater than the circumferentialspeed of the portion of the blank engaged thereby, and the severalstages of the shiftable transmission 27 cause rotation of roller 25 atselected rotary speeds at which the peripheral speed at the smallestdiameter of the frusto-conical roller 25 is the same as the peripheralspeed at the greatest diameter of roller 25 when the same was driven bythe preceding stage of the transmission.

Carriage 22 has vertical guideways 28, 29 on which a slide 30 is movablein vertical direction, and parallel to the axes of rollers 3 and 13. Afrusto-conical roller 31 is mounted on slide 30 to cooperate with roller25 in the positions illustrated in FIGS. 7 and 8. A worm gear 32 ismounted on slide 30 for rotation, but non-movable in axial direction,and is driven through a worm by an electric motor 33. Worm gear 32 hasan inner female thread meshing with a thread on a piston rod 34 of apiston 35 located in a double-acting cylinder 36 which is secured tocarriage 22. Cylinder 36 and piston 35 constitute a third servomotor bywhich slide 30 with frustoconical roller 31 can be moved toward and awayfrom frusto-conical roller 25. Roller 31 can be moved to a position inwhich rollers 25 and 31 cooperate to roll on the axial annular end facesof blank 36, as shown in FIG. 7. When rollers 31 and 25 are in theposition of FIG. 7 and engage the annular blank 38 when the same hasjust been placed in the machine and has its smallest diameter, theapices of frusto-conical rollers 25 and 31 are located on the axis 37 ofa new blank 38. As the diameter of blank 38 increases due to the rollingoperation, axis 37 travels in the plane defined by the axes of the firstrollers 3 and 13, so that the apices of the second rollers 25, 31 are nolonger located on axis 37. The upper frusto-conical roller 31 isslightly offset in a known manner relative to the lower frusto-conicalroller 25 in a direction of rotation of the blank 38 in order to C0111-pensate the turning moment produced by the rolling forces.

As best seen in FIGS. 4 and 6, sensing means are provided for sensingthe increasing size of the rolled blank 38, and include a feeler means39 having a feeler roll 48 engaging the outer peripheral surface ofblank 38, and a switching member or portion 47 having a plurality ofabutments 43, 42, 41 for respectively engaging limit switches 46, 45, 44when feeler means 39 is displaced due to the increasing diameter ofblank 38. Feeler means 39 has a flange engaged by spring 40 which urgesfeeler means 39 to move relative to carriage 22 to a position in which apair of shoulders on portion 47 abuts corre sponding abutment faces ofcarriage 22. In this manner, one end position of roll 48 is determined.Portion 47 has a rack bar 49 meshing with a pinion 50 which is mountedon a shaft 51 rotatably supported on carriage 22 and carrying anotherpinion 52 meshing with a rack bar 53 of a control bar 54 guided forlongitudinal movement on carriage 22. A projection on control bar 54cooperates with a limit switch 56 which is adjustable along a graduatedguide member 55, and can be fixed on the same in any selected positiondetermined in accordance with the scale. During the rolling operation,blank 38 rests on a plurality of supporting surfaces 57, as indicated inFIG. 2.

The machine has a hydraulic control system. Hydraulic control andoperating means for moving roller 13 toward roller 3 will now bedescribed with reference to FIG. 4.

An automatically regulated oil pump 58 pumps fluid into the line 57which has a safety valve 60. A manually operated control slide 46 isconnected to the pressure line 59, and has four different positionscontrolling the flow through the pressure line 64, the preliminarysupply line 63, the return line 62, and a discharge line 65. The returnline 62 is connected to opening 19 in piston 18, the preliminary supplyline 63 is connected with the bore of piston 18 in which the auxiliarypiston 21 is located, and the return line 64 is connected with theopening 20 in piston 18. The return line 62 has a safety valve 66, andreturn line 62 and pressure line 64 are connected to a filling valve 67.Pressure line 64 is also connected to an eleotromagnetically operatedslide valve 68 which is electrically connected to the limit switch 56.When limit switch 56 is operated, slide valve 68 connects the pressureline 64 with another electromagnetically operated slide valve 70, butinterrupts this connection when in a normal position of rest. Theelectromagnetically operated slide valve 70 connects in its normalposition of rest, the slide valve 68 with an adjustable throttle means71 which discharges into an oil container. When the manually operatedbutton 72 is actuated, slide valve 70 interrupts the connection betweenslide valve 68 and throttle 71.

Control valve 61 is shown in FIG. 4 in a position of rest in which thesupply line 59 from the oil pump 58 is connected with a discharge line65, while the other lines are closed. In a first control position,shifted to the left as viewed in FIG. 4, the connections schematicallyindicated by arrows at the right end of control valve 61 in FIG. 4, areestablished. Supply line 59 is connected with the return line 62, andlines 63 and 64 are connected with a discharge line 65, so that carriage=12 with roller 13 is retracted from the operative position shown inFIG. 4.

In a preliminary position of control valve 61, shifted one step to theright as viewed in FIG, 4, the connections are established which areindicated by the arrows in the second field from the left on valve 61 inFIG. 4. Supply line 59 is connected to the preliminary supply line 63,and connects the return line 62 with the discharge line 65, while line64 is closed.

When control valve 61 is shifted all the way to the right as viewed inFIG. 4, connections are established as indicated by the arrows in thefield at the left end of valve 61 in FIG. 4, and supply line :59 isconnected with the preliminary supply line 63 and with the pressure line64, while the return line 62 is connected with a discharge line 65.

The hydraulic control and operating means for operating slide 30 to movethe upper fiusto-conica'l roller 31 toward and away from the blank, willnow be described with reference to FIG. 5.

An oil pump 73 pumps the operating liquid into the supply line 74 whichhas a safety valve 75. The flow is controlled by a control valve 76which is manually operated, A discharge line 77, a pressure line 78leading to the upper chamber in cylinder 36, and a return line 89connected through an adjustable throttle check valve 79 with the lowerchamber in cylinder 36, are connected to the control valve 76.

The pressure line 78, which controls the axially exerted rollingpressure between rollers 25 and 31, is connected with a maximum pressurevalve 81, and with an electromagnetica'lly operated slide valve 82. Inits normal position of rest, slide valve 82 connects pressure line 78with an oil container, but when limit switch 45, see FIG. 6, is operatedby the abutment 42 of the feeler means 39, this discharge is stopped.

Control valve 7 6 has three positions. In the illustrated normalposition, the return line 80 is closed, and supply line 74 and pressureline 78 are connected with the discharge line 77. In the operativeposition in which valve 76 is during a rolling operation, valve 76 isshifted to the left as viewed in FIG. 5, and the connections indicatedby the arrows at the right end of valve 76 are made. Supply line 74 isconnected with the pressure line 78, and return line 80 is connectedwith the discharge line 77. To retract roller 31 from the blank, valve76 is shifted to the right as viewed in "FIG. 5, and the connectionsindicated at the left end of valve 76 in FIG. 5 are made. Supply line 74is connected with the return line 83, while the pressure line 78 isconnected with a discharge line 77.

The hydraulic control and operating means for moving carriage .22 withslide 30, and rollers 25, 31, are illustrated in FIG. 6.

An automatically regulated oil pump 83 pumps into a supply line 84 whichis connected to an electromagnetically operated control valve 85.Pressure line 84 is connected to a safety valve 86, and to a regulatingline 87 having a first branch line connected through an adjustablethrottle and a maximum pressure valve to an electromagneticallycontrolled slide valve 88, and a second branch connected to the pressurechamber of a pump regulator 89 which controls pump 83.

Control valve 85 is connected to a line 91 leading to theelectromagnetically operated slide valve 98, to a preliminary supplyline 92 con-nected to the right hand chamber of cylinder 24, and to areturn line 93 which is connected to the left hand chamber in cylinder24. Piston 23 is connected to the carriage 22 to move the same withrollers 25 and 31. The electromagnetically operated slide valve 90 has aposition of rest in which line 91 is directly connected to the dischargeline 94, but when limit switch 44 is operated by abutment 41, or whenlimit switch 46 is operated by abutment 43, slide valve 98 connects line91 through a check valve 95 with a return line 93, while the preliminarysupply line 92 is connected with the discharge line 94. The preliminarysupply line 92 has a safety valve 96.

The electromagnetically operated control valve 85 has three controlpositions. In the illustrated normal position of rest, supply line 84 isconnected with line 91. When control valve 85 is shifted to the right,so that the connections illustrated at the left end of control valve 85in FIG. 6 are operative, supply line 84 is connected with a preliminarysupply line 92 and with the return line 93. When control valve 85 isshifted to the left so that the connections illustrated at the right endof control valve 85 in FIG. 6 are effective, supply line 84 is connectedwith a return line 93, while the preliminary supply line 92 is connectedwith line 91. In this position, carriage 22 is withdrawn,

The pump regulator 89 of pump 83 has a piston which is biased by spring98 to move against the pump pressure prevailing in the regulating line87. When the force of spring 98 prevails, the regulating piston isshifted to increase the output of pump 83, whereas when the pumppressure exceeds a desired pressure, the regulating piston is movedagainst the action of spring 98, the pump is adjusted to pump a smalleramount of liquid so that the output of the pump is independent of thepressure encountered by the pump liquid.

A control piston 99 is biased by spring 100, and is located in acylinder which is connected to a control line 101 supplied with liquidthrough the electromagnetically operated slide valve 88. Normally, apiston rod on piston 99 abuts regulating piston 97. The stroke ofcontrol piston 99, and the force of spring 100, are dimensioned so thatcontrol piston 99 holds regulating piston 97 against the action ofspring 98 in a position in which the amount of oil pumped by pump 83 iscomparatively small, for example 40% of the rated output of the pump.

The electromagnetically operated slide valve 88 connects in its positionof rest, the control line 101 with a discharge line, while theconnection with the regulating line 87 is interrupted. When the limitswitch 46 is operated by the abutment 83 of the feeler means 39, theregulating line 87 is connected with the control line 101.

Operation Carriage 12 with roller 13, and carriage 22 with rollers 25and 31, are in the positions illustrated in FIG. 1. Slide 30 on carriage22 is in a position corresponding to the lowest position of piston 35,and the upper end position of worm gear 32. Worm gear 32 is rotated bymotor 33 in such a direction of rotation that piston 34 is downwardlymoved due to the threaded engagement between piston rod 34 and the innerthread in worm gear 32. Slide 30 moves downward due to its own weight,and such downward movement is terminated when the distance between thefrusto -conical rollers 25 and 31 corresponds to the desired axialthickness of the annular blank.

Control valve 76 is moved to the return position in which slide 30 israised by piston 35. Main roller 3 is rotated by motor 5, and the lowerfrusto-conical roller 25 is rotated by motor 26.

An annular blank 35 is placed on the supporting faces 57 with roller 13passing through the center hole in the blank. The lever means 16 withthrust bearing 16a are lowered by servomotor 15 so that bearing 16aabuts under pressure on roller 13, and prevent any bending of the shaftof roller '13 due to the rolling pressure during the rolling operation.

Control valves 81 and are shifted to the preliminary control positions.Control valve 61 is shifted one step to the right as viewed in FIG. 4 toa preliminary control position in which the oil pumped by pump 58 isguided into the preliminary supply line 63 so that auxiliary piston 21is operated to move cylinder 17, carriage 12, and roller 13 to the leftas viewed in the drawing and toward main roller 3 until the annularblank is engaged on its outer peripheral surface by main roller 3, andat its inner peripheral surface by roller 13.

The liquid displaced through bore 19 of piston 18 flows through controlvalve 61 into the discharge line 65. The preliminary filling valve 67permits the flow of liquid from a container in which an air cushionprovides pressure, through pressure line 64 into the chamber on the leftof piston 18 in cylinder 17.

Control valve 85 is shifted to the right as viewed in FIG. 6 to apreliminary control position in which pump 83 is connected with bothchambers of cylinder 24. Since the pressure surface at the end face ofpiston 23 is greater than that of the annular pressure surface of piston23 surrounding its piston rod, piston 23 moves to the left as viewed inthe drawing, and carriage 22 with frusto-conical rollers 25 and 31 ismoved toward roller 13 until rollers 25 and 31 are located on oppositesides of the annular blank 38.

When carriage 12 with roller 13 has moved so far that blank 38 isclamped between the cylindrical surfaces of rollers 13 and 3 so that theblank is located in a horizontal plane perpendicular to the axes ofrollers 3 and 13, control valves 61 and 76 are operated and shifted tocontrol position effecting therolling operations.

Control valve 61 is shifted all the way to the right as viewed in FIG.4, so that the liquid pumped by pump 58 passes from the pressure line 59into preliminary supply line 63 and pressure line 64 so that not onlyauxiliary piston 21, but also the large end free on the left side ofpiston 18 is subjected to pressure. The chamber on the other side ofpiston 18 is still connected with a discharge line 65. Slide 12 willroller 13 is slowly moved toward main roller 38, and exerts greatrolling pressure against the clamped portion of annular blank 38. Blank38 and roller 13 are rotated by main roller 3 due to the frictionalcoupling between the rollers and the blank, and the blank is rolled sothat its radial thickness is reduced, while its diameter is increased sothat the axis 37 of the blank travels to the right from the position ofFIG. 7 toward the position shown in FIG. 8.

Control valve 76 is shifted to the left so that the lower chamber ofcylinder 36 is connected with the discharge line 77 while supply line 74is connected to pressure line 78 which communicates with the uppercylinder chamber. The liquid flows through electromagnetic slide valve82 into a container. Since the liquid in the lower chamber of cylinder36 can flow out through throttle check valve 79, slide 30 withfrusto-conical roller 31 slowly moves downward until roller 31 rests onblank 38. However, no axial rolling pressure is yet exerted due to thefact that electromagnetically operated slide valve 82 is still open.

As the diameter of blank 38 increases due to the rolling action of thefirst rollers 3 and 13, the outer peripheral surface of ring 38 engagesthe feeler roll 48 so that feeler means 39 is moved relative to carriage22 out of the position shown in FIG. 6 in which shoulders of portion 47abut corresponding shoulders on carriage 22. The displaced position ofthe feeler means is shown in FIG. 4. When the diameter of the outerperipheral surface of blank 38 is so great that the outer peripheralsurface of blank 38 is in contact with the base circles offrusto-conical second rollers 25 and 31, abutment 42 of feeler means 39,47 engages and operates limit switch 45 which is electrically connectedinto the circuit of electromagnetically operated slide valve 82 andactuates the same to interrupt the connection between the pressure line78 and the container for the liquid, so that the pressure liquid isconfined in the upper chamber of cylinder 36 and provides sufiicientpressure to move piston 35 with piston rod 34, worm gear 32 and slide 30downward with frusto-conical roller 31 so that the rolling pressure isexerted by rollers 25 and 31 on blank 38 acting in axial direction toreduce the axial height or thickness of blank 38.

At the beginning of the operation, the apices of the frusto-conicalperipheral surfaces of rollers 25, 31 are located on axis 37 of blank38, as shown in FIG. 7, so that the peripheral speed at the smaller endsof frustoconical rollers 25 and 31 correspond to the circumferentialspeed of the inner peripheral surface of blank 38, while the peripheralspeeds at the larger ends of frustoconical rollers 25 and 31 correspondto the circumferential speed of the outer peripheral surface of blank38.

In accordance with the present invention, the respective speeds are notthe same, but the peripheral speed of the driven roller 25 is slightlyhigher than the circumferential speeds of the inner and outer surfacesof blank 38, so that a small relative movement takes place which,however, is tolerable at the beginning of the rolling operation duringwhich the blank is still very strong. On the other hand, when thediameter of the annular blank increases during the rolling operation,and the apices of the frustoconical rollers 31 are no longer located onthe axis 37 of blank 38, no relative movement takes place, which isdesirable since the rigidity of the blank is reduced as its diameter isincreased. Due to this feature of the invention, the relative movementbetween the surfaces of the rollers 25, 3'1 and the end faces of blank38 is reduced during the main part of the rolling operation which is anadvantage as compared to the prior art construction where substantialsliding between the engaging surfaces, and corresponding frictionallosses and heat development take place during the main part of therolling operation.

When the feeler means is slightly pushed back during the followingincrease of the diameter of blank 38, abutment 41 of feeler means 39operates limit switch 44 which is connected into the circuit ofelectro-magnetically operated slide valve so that a small amount ofliquid is pumped by pump 83 into the left chamber of cylinder 24, whilethe right chamber is connected to the discharge line The pumped amountis limited to the equilibrium between springs 98 and acting onregulating piston 97 together with control piston 99.

Carriage 22 slowly moves to the right, corresponding to the increase ofthe diameter of blank 38 so that rollers 25 and 31 remain in theposition in which the base circles thereof are located in the region ofthe outer peripheral surface of blank 38, while the peripheral surfacesof rollers 25 and 31 abut the annular end faces of blank 38 Whose radialthickness is simultaneously reduced so that the smaller ends offrusto-conical rollers 25 and 31 are not in engagement with .the annularend faces of blank 38.

If the speed of movement of carriage 22 corresponds to the increase ofthe diameter of blank 38, the desired position is maintainedcontinuously. However, if the speed of carriage 22 is greater than theincrease of the diameter of blank 38, spring 40 urges feeler means 39 tothe left as viewed in the drawing so that feeler roll 48 remains inengagement with the outer peripheral surface of blank 38. Due to therelative movement between carriage 22 with the limit switches, andfeeler means 39, limit switch 44 is released by abutment 41 so thatelectromagnetically operated slide valve 90 returns to its initialposition. Pump 83 is connected to the discharge, and carriage 22 stopsuntil the diameter of blank 38 is sufficiently increased to displacefeeler means 39 so far relative to carriage 22 that limit switch 44 isagain operated.

If the speed of movement of carriage 22 is less than the increase of thediameter of blank 38, feeler means 39 is shifted to the right afterlimit switch 44 was operated, and limit switch 46 is operated byabutment 43. Limit switch 46 is connected into the circuit of theelectromagnetically operated slide valve 88 which is actuated so thatthe pressure liquid in regulating line 87 operates regulating piston 99which is shifted against the action of spring upwards as viewed in thedrawing so that spring 98 can shift piston 97 of regulator 89 to theposition in which the maximum amount of liquid cannot determine by thesupply line 84, is pumped by pump 83. Electromagnetically operated slidevalve 90 guides the pressure liquid into the left chamber of cylinder 24so that carriage 22 is moved to the right at an increased speed whilefeeler means 39, 48 remains in engagement with blank 38, so that arelative movement between feeler means 39 and carriage 22 with the limitswitches takes place until limit switch 46 is again released by abutment43.

Due to the relative movement between the feeler means and the carriage22 and the corresponding actuation of limit switchs 44 and 46, thegreatest peripheral surface portions of frusto-conical rollers 25 and 31are auto matically held in a position in which they engage the outermostportion of the anular end faces of blank 38, so that the relationbetween the circumferential speed of the blank and the peripheral speedof the frusto-conical rollers remains constant in the region of theouter peripheral surface of blank 38.

Due to the fact that the apices of frusto-conical rollers 25 and 31 moveaway from the axis 37 of the blank, the peripheral speed at the smallerends of the frusto-conical rollers 25 and 31 is reduced as compared withthe circnmferential speed of the engaged portions of the annular endfaces of blank 38. Assuming a selected slip of relative movement of 6%which is obtained by suitable design of the transmission means 27, suchslip remains con stant in the region of the outer peripheral surface ofthe blank due to the fact that the rotary speed of the drivenfrusto-conical roller 25 is 6% too high, while the slip or relativemovement is reduced in the region of the inner peripheral surface ofblank 38 as the diameter of blank 38 increases. Consequently, therolling operation proceeds under the optimal technological conditions,without any additional load on the drive motors due to substantialslippage losses which require motors of greater power and constructionsaccording to the prior art.

As the diameter of blank 38 increases, the axial rolling pressurebetween rollers 25 and 31 is reduced corresponding to the reduced radialheight of the blank by manual or automatic adjustment of the maximumpressure valve 81. Finally, control valve 76 is shifted to its initialposition either by manual operation, or under control of a limit switch,not shown, which is operated by the feeler means when the outerperipheral surface of blank 38 has a desired diameter. When blank 38 hasthe desired outer diameter, the projection on control bar 54 operatesthe limit switch 56 so that the electromagnetically operated slide valve68 is actuated and opened whereby the liquid pumped by pump 58 flowsfrom pressure line 64 through throttle 71 into a container. Throttle 71is adjusted so that on the left side of piston 18, a pressure prevailswhich is sufiicient to hold blank 38 in frictional engagement with mainroller 3, but insufficient to cause a further rolling action reducingthe radial thickness of blank 38. This smaller pressure is maintainedduring several revolutions of blank 38, and effects a rounding of theblank to exactly circular shape with the aid of the centering rolls 6and 7. Limit switch 56 is actuated, and the radial rolling operation isterminated, as soon as blank 38 has the desired diameter selected andset by placing limit switch 56 in the corresponding position on thescale on member 55. If the blank has oval shape, limit switch 56 isactuated when the larger diameter of the blank operates feeler means 39,48. As blank 38 is deformed into exactly circular shape, the previouslygreater diameter is reduced, so that the actual diameter of the finishedblank would be smaller than the diameter set on the scale 55. This erroris corrected by operation of push button 72 which causes theelectromagnetically operated slide bar 70 to close so that the pressureliquid cannot flow through throttle 71, but passes through maximumpressure valve 69 which is adjusted to a pressure which causes a furthercontrolled rolling operation and the corresponding increase of thediameter of the now exactly circular blank 38. When the desired diameteris attained, as can be determined by observation of limit switch 56 andscale 55, the supplementary rolling operation is terminated by releasingpush button 72 so that the rounding operation is continued until controlvalve 61 is shifted to the return position. Control valves 76 and 85 arealso placed in the return position, so that carriage 12 with roller 13,and carriage 22 with slide 30 and rollers 25 and 31 return to theinitial positions. Holder frame 16 is open by operation of servomotor 15so that the finished circular blank can be removed, and a new blank canbe placed in the machine.

If a blank having a very small radial thickness is to be rolled, theaxial rolling pressure would start only after a substantial increase ofthe diameter of the blank. Thus, only a short time would be availablefor the axial rolling operation of rollers 25 and 31, particularly sinceblanks of this type also have a comparatively small final outerdiameter. In order to start the axial rolling operation on a blank ofthis type as soon as possible, a higher rotary speed is selected for thelower frusto=conica l roller 25 by shifting transmission 27 to asuitable stage, and

the rack bar 47 with the feeler roll 48 is detached from feeler means 39and then attached to the same in a displaced position in which feelerroll 48 is closer to roll 13 in the same position of carriage 22. Thisattachment is possible due to the provision of a number of equallyspaced bolts 39a which pass through corresponding sets of equally spacedbores in feeler means 39 and rack bar 47. Due to the greater distancebetween feeler roll 48 and abutment 42, slide 30 is operated to moveroller 31 toward the blank with the outer diameter of blank 33 engagingintermediate portions of the peripheral surfaces of rollers 25 and 31,and not the base circles of rollers 25 and 31. The peripheral portionsof frustoconical rollers 25 and 31 which cooperate with the outermostportions of the end faces of the blank move at a speed which is, forexample, 6% higher than the peripheral speed of the main roller 3. Dueto this adjustment, smaller blanks can be rolled under optimalconditions.

In accordance with the desired use of the ring rolling machine accordingto the invention, instead of the above explained adjustments of thetransmission 27 and of the position of the feeler roll, a greater numberof stages of a transmission may be provided, or an infinitely variabletransmission may be used together with a feeler roll whose position canbe gradually adjusted on feeler means 39. If the radial adjustment ofthe frusto-conical rollers is carried out in a continuous manner insteadof stepwise, the several limit switches are replaced by a controlelement which is continuously adjusted. It is also contemplated toprovide motors 5 and 26 with means for adjusting the rotary speed.

From the above description of the preferred embodiment of the invention,it will become apparent that the machine comprises first roller means 3and 13, second roller means 25 and 31, supporting means 22, 30 forsupporting the second rollers 25, 31, sensing means 39 to 48, andcontrol means including the several hydraulic circuits controlled by thesensing means and causing the supporting means 22, 30 to move at such aspeed that the second rollers 25, 31 move with the axial end faces ofthe blank as the diameter of the blank is increased by the rollingaction of the first rollers 3, 13 and of the second rollers 25, 31.

It will be understood that each of the elements described above, or twoor more together, may also find a useful application in other types ofring rolling machines differing from the types described above.

While the invention has been illustrated and described as embodied in aring rolling machine for maintaining a pair of rollers in contact with ablank whose diameter increases due to the rolling operation, it is notintended to be limited to the details shown, since various modificationsand structural changes may be made without departing in any way from thespirit of the present invention.

Without further analysis, the foregoing will so fully reveal the gist ofthe present invention that others can by applying current knowledgereadily adapt it for various applications without omitting featuresthat, from the standpoint of prior art, fairly constitute essentialcharacteristics of the generic or specific aspects of this inventionand, therefore, such adaptations should and are intended to becomprehended within the meaning and range of equivalence of thefollowing claims.

What is claimed as new and desired to be secured by Letters Patent is:

1. A ring rolling machine comprising, in combination, first roller meansfor engaging and rolling the inner and outer peripheral surfaces of anannular blank for increasing the diameter of the same; second rollermeans for engaging and rolling portions of the axial end faces of theannular blank; supporting means supporting said second roller means formovement in the direction in which said portions of said axial end facesmove as the diameter of said annular blank increases due to the rollingaction of said roller means; sensing means for engaging one of saidperipheral surfaces of said annular blank and being movable so as to bedisplaced by the blank as the diameter of the same increases; andcontrol means controlled by said sensing means and operatively connectedwith said supporting means for causing movement of the same in saiddirection at different speeds related to the displacement of saidsensing means in such a manner that said second roller means move withsaid portions of axial end faces as the diameter of said annular blankincreases.

2. A ring rolling machine comprising, in combination, first roller meansfor engaging and rolling the inner and outer peripheral surfaces of anannular blank for increasing the diameter of the same; second rollermeans including a pair of cooperating conical rollers for engaging androlling portions of the axial end faces of the annular blank; supportingmeans supporting said second roller means for movement in the directionin which said portions of said axial end faces move as the diameter ofsaid annular blank increases due to the rolling action of said rollermeans, and including carriage means movable in radial directioninrelation to the annular blank and supporting one of said rollers, and aslide mounted on said carriage means for movement in axial direction inrelation to the annular blank and supporting the other roller; drivemeans for rotating said one roller; means for operating said slide tomove said other roller toward said one roller so that the annular blankis rolled between said rollers; sensing means for engaging one of saidperipheral surfaces of said annular blank and being movable so as to bedisplaced by the blank as the diameter of the same increases; andcontrol means controlled by said sensing means and operatively connectedwith said supporting means for causing movement of said carriage meansat different speeds related to the displacement of said sensing means insuch a manner that said second roller means move With said portions ofaxial end faces as the diameter of said annular blank increases,

3. A ring rolling machine comprising, in combination, first roller meansfor engaging and rolling the inner and outer peripheral surfaces of anannular blank for increasing the diameter of the same; second rollermeans including a pair of cooperating frusto-conical rollers forengaging and rolling portions of the axial end faces of the annularblank, said frusto-conical rollers having the surface portion thereof ofgreater diameter located at said outer peripheral surface; supportingmeans supporting said second roller means in an operative position inwhich said greater diameter surface portions of said frusto-conicalroller are disposed at said outer peripheral surface of the blank, andalso for movement in the direction in which said portions of said axialend faces move as the diameter of the annular blank increases due to therolling action of said roller means; sensing means for engaging saidouter peripheral surface of the annular blank and being movable so as tobe displaced by the blank as the diameter of the same increases; andcontrol means controlled by said sensing means and operatively connectedwith said supporting means for causing movement of the same at differentspeeds related to the displacement of said sensing means in such amanner that said second roller means move with said portions of saidaxial end faces as the diameter of the annular blank increases tomaintain said greater diameter surface portion at said outer peripheralsurface.

4. A ring rolling machine comprising, in combination, first roller meansfor engaging and rolling the inner and outer peripheral surfaces of anannular blank for increasing the diameter of the same; second rollermeans including a pair of cooperating frusto-conical rollers forengaging and rolling portions of the axial end faces of the annularblank; supporting means supporting said second roller means for movementin the direction in which said portions of said axial end faces move asthe diameter of said annular blank increases due to the rolling actionof said roller means, and including carriage means movable in radialdirection in relation to the annular blank and supporting one of saidrollers, and a slide mounted on said carriage means for movement inaxial direction in relation to the annular blank and supporting theother roller; drive means for rotating said one roller at a rotary speedcausing a peripheral speed of said one roller slightly greater than thespeed of movement of said portions of said axial end faces at thebeginning of the rolling operation when the annular blank has a smalldiameter so that the peripheral speed of said one roller and the speedof said portions become equal as the diameter of the annular blankincreases; means for operating said slide to move said other rollertoward said one roller so that the annular blank is rolled between saidrollers; sensing means for engaging one of said peripheral surfaces ofsaid annular blank and being movable so as to be displaced by the blankas the diameter of the same increases; and control means controlled bysaid sensing means and operatively connected with said supporting meansfor causing movement of the same in said direction at different speedsrelated to the displacement of said sensing means in such a manner thatsaid second roller means move with said portions of axial end faces asthe diameter of said annular blank increases.

5. A ring rolling machine comprising, in combination, first roller meansfor engaging and rolling the inner and outer peripheral surfaces of anannular blank for increasing the diameter of the same; second rollermeans including a pair of cooperating frusto-conical rollers forengaging and rolling portions of the axial end faces of the annularblank; supporting means supporting said second roller means for movementin the direction in which said portions of said axial end faces move asthe diameter of the annular blank increases due to the rolling action ofsaid roller means; drive means for rotating one of said rollers at arotary speed causing a peripheral speed of said one roller slightlygreater than the speed of movement of the axial end faces of the annularblank at the beginning of the rolling operation when the annular blankhas a small diameter so that the peripheral speed of said one roller andthe speed of said axial end faces become equal as the diameter of theannular blank increases; sensing means for engaging one of saidperipheral surfaces of the annular blank and being movable so as to bedisplaced by the blank as the diameter of the same increases; andcontrol means controlled by said sensing means and operatively connectedwith said supporting means for causing movement of the same at a speedrelated to the displacement of said sensing means in such a manner thatsaid second roller means move with said portions of axial end faces asthe diameter of the annular blank increases.

6. A ring rolling machine comprising, in combination, a pair of firstrollers for engaging and rolling the inner and outer peripheral surfacesof an annular blank for increasing the diameter of the same, said firstrollers having axes located in a first plane which is radial withrespect to the annular blank so that the annular blank rotates in asecond plane perpendicular to said first plane about an axis of rotationlocated in said first plane and travelling away from said first rollersas the diameter of the blank increases; a pair of second rollers forengaging and rolling portions of the axial end faces of the annularblank, said second rollers having axes located in said first plane;supporting means supporting said second rollers for movement in saidfirst plane in the direction in which said axis of the annular blanktravels; sensing means for engaging one of said peripheral surfaces ofthe blank as the diameter of the same increases; and control meanscontrolled by said sensing means and operatively connected with saidsupporting means for causing movement of the same in said direction atdifferent speeds related to the displacement of said sensing means insuch a manner that said second rollers move with said portions of axialend faces as the diameter of the annular blank increases.

7. A ring rolling machine comprising, in combination, a pair of firstrollers for engaging and rolling the inner and outer peripheral surfacesof an annular blank for increasing the diameter of the same, said firstrollers having axes located in a first plane which is radial withrespect to the annular blank so that the annular blank rotates in asecond plane perpendicular to said first plane about an axis of rotationlocated in said first plane and travelling away from said first rollersas the diameter of the blank increases; a pair of frusto-conical secondrollers for engaging and rolling portions of the axial end faces of theannular blank, said second rollers having axes located in said firstplane and defining angles with each other and with said second plane;supporting means supporting said second rollers for movement in saidfirst plane in the direction in which said axis of the annular blanktravels; sensing means for engaging one of said peripheral surfaces ofthe blank as the diameter of the same increases; and control meanscontrolled by said sensing means and operatively connected with saidsupporting means for causing movement of the same in said first plane atdifferent speeds related to the displacement of said sensing means insuch a manner that said second rollers move with said portions of axialend faces as the diameter of the annular blank increases.

8. A ring rolling machine comprising, in combination, first roller meansfor engaging and rolling the inner and outer peripheral surfaces of anannular blank for increasing the diameter of the same; second rollermeans for engaging and rolling portions of the axial end faces of theannular blank; supporting means supporting said second roller means formovement in the direction in which said portions of said axial end facesmove as the diameter of the annular blank increases due to the rollingaction of said roller means; sensing means including a feeler meansmounted on said sup porting means for movement in said directionrelative to said supporting means and means biasing said feelermeansinwardly toward the blank to engage the outer peripheral surface ofthe annular blank so as to be displaced by the same as the diameter ofthe same increases; and control means controlled by said sensing meansin positions displaced relative to said supporting means and operativelyconnected with said supporting means for causing movement of the same atdifferent speeds related to the relative displacement between saidsensingmeans and said suppoiting means in such a manner that said secondroller means move with said portions of said axial end faces as thediameter of the annular blank increases.

9. A ring rolling machine comprising, in combination, first roller meansfor engaging and rolling the inner and outer peripheral surfaces of anannular blank for increasing the diameter of the same; second rollermeans for engaging and rolling portions of the axial end faces of theannular blank; supporting means supporting said second roller means formovement in the direction in which said portions of said axial end facesmove as the diameter of the annular blank increases due to the rollingaction of said roller means; sensing means including a feeler meansmounted on said supporting means for movement in said direction relativeto said supporting means and means biasing said feeler inwardly towardthe blank to engage the outer peripheral surface of the annular blank soas to be displaced by the same as the diameter of the same increases;and control means including a series of limit switches successivelyoperated by said feeler means as the same is displaced relative to saidsupporting means, and operating means controlled by said limit switchesand operatively connected with said supporting means for caus-v ingmovement of the same at different speeds related to the displacement ofsaid sensing means in such a manner that said second roller means movewith said portions of said axial end faces as the diameter of theannular blank increases.

10. A ring rolling machine comprising, in combination, first rollermeans for engaging and rolling the inner and outer peripheral surfacesof an annular blank for increasing the diameter of the same; secondfrustoconical roller means for engaging and rolling portions of theaxial end faces of the annular blank; supporting means supporting saidsecond roller means for move ment in the direction in which saidportions of said axial end faces move as the diameter of the annularblank increases due to the rolling action of said roller means; sensingmeans including a feeler means mounted on said supporting means formovement in said direction relative to said supporting means and springmeans acting on said feeler means to urge the same to engage the outerperipheral surface of the annular blank so as to be displaced by thesame as the diameter of the same increases; and control means includinga series of limit switches successively operated by said feeler means asthe same is displaced relative to said supporting means, and operatingmeans controlled by said limit switches and operatively connected withsaid supporting means for causing movement of the same at differentspeeds related to the displacement of said sensing means in such amanner that said second roller means move with said portions of axialend faces as the diameter of the annular blank increases, said springmeans holding said feeler means in engagement with the outer peripheralsurface of the annular blank when the movement of said supporting meanscauses movement of said second roller means at a speed greater than thespeed of displacement of said portions of said axial end faces wherebysaid speed of said supporting means is adjusted.

11. A ring rolling machine comprising, in combination, a pairof firstrollers for engaging and rolling the inner and outer peripheral surfacesof an annular blank for increasing the diameter of the same, said firstrollers having axes located in a first plane which is radial withrespect to the annular blank so that the annular blank rotates in asecond plane perpendicular to said first plane about an axis of rotationlocated in said first plane and travelling away from said first rollersas the diameter of the blank increases; a pair of frustoconical secondrollers for engaging and rolling portions of the axial end faces of theannular blank, said sec- 0nd rollers having axes located in said firstplane and defining angles with each other and with said second plane;supporting means supporting said second rollers for movement in saidfirst plane in the direction in which said axis of the annular blanktravels; sensing means including a feeler means mounted on saidsupporting means for movement in said direction relative to saidsupporting means and spring means acting on said feeler means to urgethe same to engage the outer peripheral surface of the annular blank soas to be displaced by the same as the diameter of the same increases;and control means including a series of limit switches successivelyoperated by said feeler means as the same is displaced relative to saidsupporting means, and operating means controlled by said limit switchesand operatively connected with said supporting means for causingmovement of the same at different speeds related to the displacement ofsaid sensing means in such a manner that said second rollers move withsaid portions of axial end faces as the diameter of the annular blankincreases, said spring means holding said feeler means in engagementwith the outer peripheral surface of the annular blank when the movementof said supporting means causes movement of said second roller means ata speed '15 greater than the speed of displacement of said portions ofsaid axial end faces whereby said speed of said supporting means isadjusted.

12. A ring rolling machine comprising, in combination, first rollermeans for engaging and rolling the inner and outer peripheral surfacesof an annular blank for increasing the diameter of the same; secondroller means including a pair of cooperating rollers for engaging androlling portions of the axial end faces of the annular blank; supportingmeans supporting said sec ond roller means for movement in the directionin which said portions of said axial end faces move as the diameter ofthe annular blank increases due to the rolling action of said rollermeans, and including carriage means movable in radial direction inrelation to the annular blank and supporting one of said rollers, and aslide mounted on said carriage means for movement in axial direction inrelation to the annular blank and supporting the other roller; drivemeans for rotating said one roller; means for operating said slide tomove said other roller toward said one roller so that the annular blankis rolled between said rollers; sensing means including a feeler meansmounted on said supporting means for movement in said direction relativeto said supporting means and adapted to engage the outer peripheralsurface of the annular blank so as to be displaced by the same as thediameter of the same increases; and control means including a series oflimit switches successively operated by said feeler means as the same isdisplaced, and operating means controlled by said limit switches andoperatively connected with said supporting means for causing movement ofsaid carriage means at difierent speeds related to the displacement ofsaid sensing means in such a manner that said second roller means movewith said portions of axial end faces as the diameter of the annularblank increases.

13. A ring rolling machine as set forth in claim 12 wherein said movingmeans include electromagnetic means controlled by said limit switches sothat each successively operated limit switch causes movement of saidcarriage at a higher speed.

14. A ring rolling machine as set forth in claim 13 and including aservo motor for moving said other roller toward said one roller, andmeans for controlling said servo motor and being actuated by one of saidlimit switches.

15. A ring rolling machine as set forth in claim 14 wherein said servomotor means has a first position in which said rollers engage said blankand a second position in which said rollers roll said blank.

16. A ring rolling machine as set forth in claim 15 wherein said feelermeans are mounted on said carriage for adjustment relative to the same,and wherein said drive means include variable transmission means.

17. A ring rolling machine as set forth in claim 12 16 and including afirst motor for rotating said main roller, and wherein said drive meansincludes a second motor.

18. A ring rolling machine as set forth in claim 12 and including ascale member; a limit switch operated by said feeler means and mountedon said scale member for adjustment to a position corresponding to adesired outer diameter of said blank, said operating means includingelectromagnetic means electrically connected to said last mentionedlimit switch so that said operating means is stopped when said blank hasa desired and selected outer diameter.

19. A ring rolling machine as set forth in claim 18 and including springmeans acting on said feeler means to urge the same into engagement withthe outer peripheral surface with said blank, said feeler means beingmounted on said carriage movable relative to the same in the directionof movement of said carriage.

20. In a ring rolling machine, in combination, roller means for engagingand rolling at least one surface portion of an annular blank which movesduring rolling in a predetermined direction; supporting means supportingsaid roller means for movement in said predetermined direction; meansfor moving said supporting means in said predetermined direction at anyone of a plurality of predetermined speeds; sensing means actuated bymovement of said blank in said predetermined direction; and controlmeans controlled by said sensing means and actuating said moving meansto change the speed of movement of said supporting means from a slowerspeed to a faster speed when said blank moves in said predetermineddirection faster than said roller means.

21. In a ring rolling machine, in combination, roller means for engagingand rolling at least one surface portion of an annular blank which movesduring rolling in a predetermined direction; supporting means supportingsaid roller means for movement in said predetermined direction; meansfor moving said supporting means in said predetermined direction at anyone of a plurality of predetermined speeds; sensing means actuated bymovement of said blank in said predetermined direction; and controlmeans controlled by said sensing means and actuating said moving meansto change the speed of movement of said supporting meansfrom a slowerspeed to a faster speed when said blank moves in said predetermineddirection faster than said roller means and to stop movement of saidsupporting means when said blank moves in said direction slower thansaid roller means.

References Cited by the Examiner UNITED STATES PATENTS 2,132,370 10/38Hubbard -5 2,307,191 1/43 Bell et al. 80--5 2,776,585 1/57 Kendall 805CHARLES W. LANHAM, Primary Examiner.

1. A RING ROLLING MACHINE COMPRISING, IN COMBINATION, FIRST ROLLER MEANSFOR ENGAGING AND ROLLING THE INNER AND OUTER PERIPHERAL SURFACES OF ANANNULAR BLANK FOR INCREASING THE DIAMETER OF THE SAME; SECOND ROLLERMEANS FOR ENGAGING AND ROLLING PORTIONS OF THE AXIAL END FACES OF THEANNULAR BLANK; SUPPORTING MEANS SUPPORTING SAID SECOND ROLLER MEANS FORMOVEMENT IN THE DIRECTION IN WHICH SAID PORTIONS OF SAID AXIAL END FACESMOVE AS THE DIAMETER OF SAID ANNULAR BLANK INCREASES DUE TO THE ROLLINGACTION OF SAID ROLLER MEANS; SENSING MEANS FOR ENGAGING ONE OF SAIDPERIPHERAL SURFACES OF SAID ANNULAR BLANK AND BEING MOVABLE SO AS TO BEDISPLACED BY THE BLANK AS THE DIAMETER OF THE SAME INCREASES; ANDCONTROL MEANS CONTROLLED BY SAID SENSING MEANS AND OPERATIVELY CONNECTEDWITH SAID SUPPORTING MEANS FOR CAUSING MOVEMENT OF THE SAME IN SAIDDIRECTION AT DIFFERENT SPEEDS RELATED TO THE DISPLACE-